WO2006015483A1 - Guide de transmission a chaine composite - Google Patents

Guide de transmission a chaine composite Download PDF

Info

Publication number
WO2006015483A1
WO2006015483A1 PCT/CA2005/001229 CA2005001229W WO2006015483A1 WO 2006015483 A1 WO2006015483 A1 WO 2006015483A1 CA 2005001229 W CA2005001229 W CA 2005001229W WO 2006015483 A1 WO2006015483 A1 WO 2006015483A1
Authority
WO
WIPO (PCT)
Prior art keywords
guide
piston
tensioner assembly
set forth
spring
Prior art date
Application number
PCT/CA2005/001229
Other languages
English (en)
Inventor
Jacek S. Komorowski
Witold Gajewski
Original Assignee
Litens Automotive Partnership
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Litens Automotive Partnership filed Critical Litens Automotive Partnership
Priority to CA2575844A priority Critical patent/CA2575844C/fr
Priority to KR1020077003312A priority patent/KR101224757B1/ko
Priority to PL05772272T priority patent/PL1779002T3/pl
Priority to EP05772272A priority patent/EP1779002B1/fr
Priority to BRPI0514261-0A priority patent/BRPI0514261A/pt
Priority to JP2007525136A priority patent/JP2008509358A/ja
Priority to US11/659,647 priority patent/US7942770B2/en
Publication of WO2006015483A1 publication Critical patent/WO2006015483A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0806—Compression coil springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0812—Fluid pressure

Definitions

  • the present invention relates generally to tensioners, and more particularly, to timing tensioners that produce tension forces of varying magnitude.
  • chain systems Typical chain or belt systems (hereinafter collectively referred to as “chain systems”) are known in the art for use in automotive applications. These chain systems include tensioners that apply a uniform load to a slack side of the chain or belt, which maintains the tension of the chain or belt above a minimum value required to drive various components attached to the belt system. Additionally, tensioners are used in non-synchronized drive systems to prevent slippage and power transmission loss. And finally, tensioners are commonly utilized in accessory drive systems, and timing chain or belt systems of an automobile.
  • a guide 116 is in contact with an endless drive element 120, such as a chain or belt, along a running surface.
  • An actuator 118 engages the guide 116, and adjusts the position of the guide 116 to vary the tension in the chain 120.
  • the guide 116 is pivotally attached to the engine and a hydraulic actuator 118 engages the guide 116 to angularly displace the guide 116 about the pivot point 130.
  • the hydraulic actuator 118 includes a spring 119 to assist in maintaining the guide 116 in engagement with the chain 120.
  • the applied force to the chain 120 diminishes, primarily as a result of reduced spring force, as the guide 116 moves in a chain engaging direction.
  • the range of applied forces can vary from a low and high value difference at various positions in a significant amount. Such a wide range of applied forces results in varying tensions within the chain.
  • the chain has a high tension that may lead to chain stretch over time, as well as increased frictional wear on various components of a timing chain system, such as the bearings of a crank or camshaft.
  • NASH noise, vibration and harshness
  • a tensioner assembly for a drive system including an endless drive element such as a chain or belt, of an internal combustion engine, that provides an increasing applied force to the drive system to maintain relatively constant tension in the endless drive element over the life of the endless drive element.
  • a tensioner assembly for a drive system including an endless drive element such as a chain or belt, of an internal combustion engine, that includes a hydraulic actuator, which actuator is fixedly secured to the internal combustion engine.
  • the hydraulic actuator includes a piston that is moveable between retracted and extended positions. The piston generates a force.
  • a pivoting guide operatively extends between the chain of the drive system and the piston. The pivoting guide applies a first portion of the force against the chain.
  • a lever is operatively connected to the piston between the piston and the pivoting guide. The lever translates the force from the piston to the pivoting guide.
  • the tensioner assembly also includes a cam member that is pivotally coupled to the housing and is slidingly engaged with the pivoting guide.
  • the cam member abuts the lever such that movement of the lever by the piston pivots the cam member in a manner that applies a second portion of the force against the pivoting guide, whereby as the guide pivots in a tensioning direction, the force increases, thereby maintaining a generally uniform tension in the endless drive element.
  • a tensioner assembly including a hydraulic actuator operatively mountable to an engine.
  • the hydraulic actuator has a piston moveable between retracted and extended positions in response to oil pressure of the engine, and a spring urging the piston towards the extended position.
  • a guide has a first end pivotally mountable to the engine and a second end distal from the first end.
  • the piston operatively engages the second end of the guide to torque the guide into engagement with the endless drive element and maintain tension therein.
  • a biasing assembly engages the guide and cooperates with the hydraulic actuator to apply a force to the guide, effecting an increasing torque, as the piston moves towards the extended position thereby maintaining a generally uniform tension in the endless drive element.
  • a biasing assembly for the tensioner assembly that includes a lever pivotally connected to the guide and engaging the piston and a pivotally mounted cam.
  • the cam slidingly engages with the guide, and pivotally engages with the lever.
  • the lever primarily urges the guide in an engaging direction and pivots the cam to secondarily urge the guide in a chain engaging direction.
  • a biasing assembly for the tensioner assembly that includes a spring, and a cap on each end of the spring.
  • the caps pivotally mount the spring to the second end of said guide.
  • the spring generates a spring force that initially is directed to act against an actuator force generated by the hydraulic actuator. As the piston moves to the extended position, the spring rotates directing the spring force to act in conjunction with the actuator force.
  • Figure 1 is a sectional side view of a timing system and engine including the tensioner assembly and pivoting guide of the present invention
  • Figure 2 is an exploded perspective view of the tensioner assembly and pivoting guide of the present invention
  • Figure 3 is a side view of the tensioner assembly and guide of the present invention with the piston in the retracted position;
  • Figure 4 is a side view of the tensioner assembly and pivoting guide of the present invention with the piston in the extended position;
  • Figure 5 is a force diagram of a prior art guide and the guide of the present invention with the force in Newtons applied to the guide plotted as a function of the position of the guide;
  • Figure 6 is a partial side view of a prior art tensioner assembly and guide
  • Figure 7 is an exploded view of a second embodiment of the present invention.
  • Figure 8 is plan view of the embodiment of Figure 7, with the hydraulic actuator in the retracted position.
  • Figure 9 is a plan view of the embodiment of Figure 7, with the hydraulic actuator in the extended position.
  • the drive system 4 includes an endless drive element, such as a chain 6 linking a crankshaft 8 to camshafts 10. Although the pictured embodiment details a chain 6, it is to be understood that other endless drive elements, including a belt, may also be utilized by the present invention.
  • the chain 6 engages rotatable elements or sprockets 12, 14 associated with the crankshaft 8 and camshafts 10, respectively.
  • the chain 6 transfers rotation from the crankshaft 8 to the camshafts 10.
  • the chain 6 is disposed in a circuitous path about the sprockets 12, 14 with a pivoting guide 16 and tensioner assembly, generally indicated at 18, positioned on a slack side 20 of the chain 6, relative to the crankshaft 8, and a fixed guide 22 positioned on a tight side 24 of the chain 6.
  • the tensioner assembly 18 applies a force to the chain 6, through the pivoting guide
  • the pivoting guide 16 includes an arcuate guide surface 26 including a first end 28 that is pivotally attached to the internal combustion engine 2 about a pivot point 30 and a second end 32 spaced from the first end 28.
  • the pivoting guide 16 may include a series of roller members replacing the arcuate guide surface 26.
  • the tensioner assembly 18 is attached to the internal combustion engine 2 at a position toward the second end 32 of the pivoting guide 16.
  • the tensioner assembly 18 includes a hydraulic actuator 36, which is fixedly secured to the internal combustion engine 2.
  • Hydraulic actuator 36 includes a sliding piston 34 and a compression spring 35, (see Fig. 7) as is conventional in the art.
  • the tensioner assembly 18 includes a hydraulic actuator 36, although pneumatic and other actuators may be utilized by the present invention.
  • the piston 34 is operatively connected to the engine oil supply of the engine 2.
  • Engine oil is delivered under pressure to the hydraulic actuator 36, which causes movement of the piston 34 with respect to the housing of hydraulic actuator 36.
  • the piston 34 is preferably bi-directional, meaning that the piston 34 is moveable between a retracted position, as shown in Figure 3 and an extended position, as shown in Figure 4.
  • the housing of hydraulic actuator 36 has a connection member
  • the guide 16 includes a structural portion 38 supporting the arcuate guide surface 26.
  • Arcuate guide surface includes a chain engaging portion 40 disposed between side flanges 42 extending from the structural portion 38.
  • Chain engaging portion 40 may include a wear resistant material for resisting frictional wear due to constant engagement with the chain 6.
  • Guide 16 has a sliding surface 78 on the underside of structural portion 38 that receives the cam 46.
  • Sliding surface 78 may be planar or have a contour or shape that can be utilized to further manipulate force distribution between the cam 46 and the sliding surface
  • the tensioner assembly 18 includes a biasing assembly 43.
  • Biasing assembly 43 comprises a lever 44 and cam 46.
  • the lever 44 is generally S-shaped and includes a trough 50 defined by generally parallel sides 52 and a bottom 54.
  • the lever 44 includes a first portion 56 proximate the first end 28 of the pivoting guide 16 and a second portion 58 angularly displaced relative to the first portion 56.
  • the first portion 56 of the lever 44 includes aligned holes 60 formed through the sides 52 of the trough 50 for pivotally attaching the lever 44 to the movable guide 16 using a guide pin 62.
  • the second portion 58 of the lever 44 is generally L-shaped that defines a bight 59 and terminates at a cam engaging portion 64.
  • the cam engaging portion 64 includes side extensions 63, 65. The side extensions 63, 65 overlap the connection member 48 to maintain a proper alignment of the lever 44 with respect to the pivoting guide 16 and the piston 34.
  • the piston 34 engages the bottom 54 of the lever 44 to pivot the pivoting guide 16 about the pivot point 30.
  • the embodiment of the lever 44 shown in the Figures is pivotally attached at the first portion 56 to the pivoting guide 16, the first portion 56 of the lever 44 may alternatively be pivotally attached to the internal combustion engine 2.
  • the cam 46 is preferably V-shaped having two legs 68, 70 meeting at a vertex 72.
  • First leg 68 of the cam 46 terminates at a lever engaging portion 74 that is nested within bight
  • the second leg 70 of the cam 46 terminates at a second leg hole 76 for pivotally attaching to the distal end 49 of the connection member 48 of the housing of the hydraulic actuator 36.
  • the vertex 72 of the cam 46 engages a sliding surface 78 This abutting engagement of the vertex 72 with the sliding surface 78 affects the movement of the pivoting guide 16.
  • vertex 72 of the cam 46 may be shaped or replaced with a roller type bearing to engage the pivoting guide 16.
  • the tensioner assembly 18 fits in the space occupied by the prior art tensioner 118. This characteristic is commercially desirable, as an internal combustion engine layout does not need to be altered to accommodate the tensioner assembly
  • the hydraulic actuator 36 receives oil under pressure from the engine.
  • the piston 34 converts the pressure to a force that is transmitted to the lever 44.
  • the endless drive element 6 will stretch, allowing the piston 34 to move from the retracted position, shown in Figure 3 to the extended position, shown in
  • the lever 44 also transmits a second portion of the force, through the cam 46, represented by the vector F2 at the vertex 72 thereof.
  • the varying magnitude is attributed to movement of the cam 46 about the connection member 48 and along the sliding surface 78 of the pivoting guide 16 as the piston 34 extends.
  • the mechanical advantage of the cam 46, in relation to the pivoting guide 16 increases as the piston 34 extends, thereby increasing the magnitude of F3. More importantly, the effect of the increasing magnitude of F3 is amplified since F3 is applied to the pivoting guide 16 at a point further out from the pivot point 30 and thereby has a larger moment arm as compared with force Fl.
  • the torque available that can be applied to the endless drive element 6 starts at a minimum level and increases as the endless drive element 6 wears and stretches.
  • the variation of the magnitude of the F3 may also be described as a ratio of the F3 and F2 vectors.
  • the ratio of the vectors F3 and F2 changes as the piston 34 extends and retracts. As the piston 34 extends the ratio of F3 to F2 approaches a more 1 to 1 relationship as denoted by the similar lengths of the F3 and F2 vectors in Figure 4.
  • FIG 5 there is shown a diagram of the force applied to a guide as a function of position for the tensioner assembly 18 and pivoting guide 16 of the present invention (solid line) and a prior art tensioner 118 and guide 116 (dashed line), shown in Figure 6.
  • the slope of the prior art force curve is much greater. In other words, there is greater variation of the force applied to the guide 116 as the position changes, than the tensioner assembly 18 and pivoting guide 16 of the present invention.
  • the lessening in variation of the force of the present invention allows for a reduction in the force applied to the pivoting guide 16 at an upper limit and also an increase in the force applied to the pivoting guide 16 at a lower limit.
  • the decreased variation of force applied to the pivoting guide 16 allows the tension within the chain 6 to be maintained in a more uniform state, reducing wear on components, as well as reducing noise generated by the drive system 4.
  • the biasing assembly 243 generally comprises a compression spring 246 and a pair of caps 248.
  • Caps 248 each has an arcuate end extending from a cylindrical portion. The cylindrical portion frictionally engages within the inside diameter of the spring 246.
  • the pivoting guide 16 is the same as the conventional prior art guide 116 with the exception that a hook structure 280 is formed on the second distal end of the guide. The hook structure 280 pivotally receives one of the caps 248.
  • the hydraulic actuator 36 is the same as the first embodiment, except that the housing has a pivot structure 250 that receives the other of the caps 248.
  • FB will change direction to a point where FB will act through the pivot point 30.
  • the spring 246 will be compressed to a maximum extent but FB will have no effect on the operation of the tensioner assembly 218.
  • FB will be directed to act in the same direction relative to the pivot point 30 and will work in conjunction with and add to the force of the hydraulic actuator 36.
  • the overall effect of the biasing assembly is to present a tensioner assembly where the torque available for tensioning the endless drive element starts at a minimum level and increases as the endless drive element wears and stretches, thereby maintaining a relatively constant tension in the endless drive element.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Abstract

La présente invention a trait à un ensemble de mise sous tension pour un système de commande, comportant une chaîne, un moteur à combustion interne, comprenant un boîtier qui est solidarisé de manière inamovible au moteur à combustion interne. Un piston est disposé au sein du boîtier. Le piston est mobile entre des positions escamotée et déployée. Le piston génère une force. Un guide pivotant s'étend en fonctionnement entre la chaîne du système de commande et le piston. Le guide pivotant applique une première portion de la force contre la chaîne. Un levier est relié en fonctionnement au piston entre le piston et le guide pivotant. Le levier transfère de la force du piston au guide pivotant. L'ensemble de mise sous tension comporte également un organe de came qui est relié en pivotement au boîtier et est en engagement coulissant avec le guide pivotant. L'organe de came est adjacent au levier de sorte que le déplacement du levier par le piston entraîne le pivotement de l'organe de came de manière à entraîner l'application d'une deuxième portion de la force contre le guide pivotant avec une ampleur variante.
PCT/CA2005/001229 2004-08-13 2005-08-10 Guide de transmission a chaine composite WO2006015483A1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
CA2575844A CA2575844C (fr) 2004-08-13 2005-08-10 Guide de transmission a chaine composite
KR1020077003312A KR101224757B1 (ko) 2004-08-13 2005-08-10 복합 체인 구동 가이드
PL05772272T PL1779002T3 (pl) 2004-08-13 2005-08-10 Złożona prowadnica napędu łańcucha
EP05772272A EP1779002B1 (fr) 2004-08-13 2005-08-10 Guide de transmission a chaine composite
BRPI0514261-0A BRPI0514261A (pt) 2004-08-13 2005-08-10 conjunto tensor para um sistema de acionamento
JP2007525136A JP2008509358A (ja) 2004-08-13 2005-08-10 複合チェーン駆動ガイド
US11/659,647 US7942770B2 (en) 2004-08-13 2005-08-10 Compound chain drive guide

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US60125104P 2004-08-13 2004-08-13
US60/601,251 2004-08-13

Publications (1)

Publication Number Publication Date
WO2006015483A1 true WO2006015483A1 (fr) 2006-02-16

Family

ID=35839100

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CA2005/001229 WO2006015483A1 (fr) 2004-08-13 2005-08-10 Guide de transmission a chaine composite

Country Status (9)

Country Link
US (1) US7942770B2 (fr)
EP (1) EP1779002B1 (fr)
JP (1) JP2008509358A (fr)
KR (1) KR101224757B1 (fr)
CN (1) CN100507311C (fr)
BR (1) BRPI0514261A (fr)
CA (1) CA2575844C (fr)
PL (1) PL1779002T3 (fr)
WO (1) WO2006015483A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006033125A1 (de) * 2006-07-18 2008-01-24 Schaeffler Kg Spanneinrichtung für ein Zugmittel, insbesondere einen Riemen oder eine Kette
US8137225B2 (en) * 2008-04-14 2012-03-20 Honda Motor Co., Ltd. Chain tensioner device
US8475307B2 (en) * 2006-08-23 2013-07-02 Iwis Motorsysteme Gmbh & Co. Kg Tensioning rail for a chain drive with a bridging guide channel section as a pressing region

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DE102005035076B4 (de) * 2005-07-21 2013-01-31 Weber Technology Ag Spannsystem
JP5670906B2 (ja) 2008-11-17 2015-02-18 ライテンズ オートモーティブ パートナーシップ 螺旋状コイルクラッチとクラッチ面との係合を行うアクチュエータを備える螺旋状コイルクラッチ組立体
ATE542728T1 (de) * 2009-11-20 2012-02-15 Iwis Motorsysteme Gmbh & Co Kg Spannvorrichtung mit verschwenkbarer gelenkverbindung
EP2518368B1 (fr) * 2011-04-27 2015-01-14 IWIS Motorsysteme GmbH & Co. KG Unité de montage pour un entraînement par chaîne
DE102011075155B4 (de) * 2011-05-03 2019-12-19 Schaeffler Technologies AG & Co. KG Montageeinheit für einen Zugmitteltrieb und Zugmitteltrieb
KR101405235B1 (ko) * 2013-07-18 2014-06-19 현대자동차 주식회사 유압식 타이밍 체인 텐셔너 및 타이밍 체인 장치
JP2019184066A (ja) * 2018-04-09 2019-10-24 ボーグワーナー インコーポレーテッド レバーを備えた油圧テンショナアーム
JP2022139454A (ja) * 2021-03-12 2022-09-26 トヨタ自動車株式会社 クランクスプロケット及びクランクスプロケットの取付構造

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006033125A1 (de) * 2006-07-18 2008-01-24 Schaeffler Kg Spanneinrichtung für ein Zugmittel, insbesondere einen Riemen oder eine Kette
US8475307B2 (en) * 2006-08-23 2013-07-02 Iwis Motorsysteme Gmbh & Co. Kg Tensioning rail for a chain drive with a bridging guide channel section as a pressing region
US8137225B2 (en) * 2008-04-14 2012-03-20 Honda Motor Co., Ltd. Chain tensioner device
US8771118B2 (en) 2008-04-14 2014-07-08 Honda Motor Co., Ltd. Chain tensioner device

Also Published As

Publication number Publication date
CA2575844A1 (fr) 2006-02-16
CA2575844C (fr) 2013-05-28
US7942770B2 (en) 2011-05-17
BRPI0514261A (pt) 2008-06-03
CN101002038A (zh) 2007-07-18
KR20070044010A (ko) 2007-04-26
JP2008509358A (ja) 2008-03-27
EP1779002A1 (fr) 2007-05-02
EP1779002B1 (fr) 2011-06-01
KR101224757B1 (ko) 2013-01-21
CN100507311C (zh) 2009-07-01
EP1779002A4 (fr) 2010-10-06
PL1779002T3 (pl) 2011-10-31
US20080081717A1 (en) 2008-04-03

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